Shuttle box mechanism for looms



6C. 7, 1937. WlGET I SHUTTLE BOX MECHANISM FOR LOOMS 2 Sheets-Shet 1 Filed Aug. 12, 1936 %ENTOR B i I y 1 l 5 ATT RNEYS Dec. 7,1937. 5, wlGET SHUTTLE BOX MECHANISM FOR LOOMS Filed Aug; 12, 1936 2 Sheets-Sheet 2 %INVENTOR B Z ATT RNEYS i Patented Dec. 7, 19 37 PATENT OFFICE 7 2,101,663 7 SHUTTLE BOX MECHANISM ronl LooMs Georg Wiget, Arbon,

Societe Switzerland, (assignor to Anonyme Adolphe Saurer, Arbon,

Switzerland, a corporation of Switzerland Application August 12, 19%, "Serial No. 95,542 In Germany September 12, 1935 4 Claims.

present invention in which a reciprocating toothed member or driving gear cooperates with a driven gear which has members side by side so mutilated that the drivinggear may operate idly when in alignment with one of suchgear members and 16 yet a complete half rotation of the driven gear shall be assured. The toothed segments of the driven gear overlap at each end by at least one tooth so that the driven gear is at all times in engagement with the driving gear, whereby the" occurrence of shocks and blows, due to the reengagement of the driving gear with the driven gear, is avoided, the longitudinal shifting of the driven gear to bring one or the other of the mutilated members into engagement with the driv- 5 ing gear taking place during the idling movement of the driving gear. Through the embodiment of this invention in a. shuttle box mechanism .it is possible to operate the loom at'higher speeds than is ordinarily possible, with a corresponding increase in the output of the loom. Provision is made whereby the driven gear is heldfrom rotation during the idling movement of the driving gear.

Different embodiments of the invention are illustrated in the accompanying drawings, in

which: 7

Figure 1 is a view in sectional elevation ,ona plane indicated by the broken line I-I of Figure 2; i

Figure 2 is a viewof the same parts as seen from the left hand in Figure], with some parts in section.

Figure 3 is a detail view of some of the parts shown in Figures 1 and 2 as seen from the right hand in Figure 1.

Figure 4 is a detail view ona larger scale of parts to be referred to. I

Figure 5 is a detail view of some of ,the'parts shown in Figure 1, but in a diiferent position.

Figure 6 is a detail view in section of some of the parts shown'in the lower right hand-portion of Figure 2, butin a different position.

Figure 7 is a partly diagrammatic view illustrating the CODYIGCtiOIiSfOI" shifting the shuttle box.

I Figure Sis a partly diagrammatic view illustrating an embodiment of the invention in which the driving gear reciprocates in a right line.

Figure 9is a detail view illustrating a different embodiment of the invention in which the reciprocating driving gear is shown as a portion of a disc and in engagement with three driven gears arranged peripherally;

In the embodiment of the invention illustrated in Figures 1-7 the supporting frame or housing I hasmounted therein a driving shaft 2, to which are secured cams 3 and 4 which cooperate, respectively, with rollers 5 and 6 of a rocker lever I which is mounted on ashaft 8 and embodies two separated gear segments 9 and I0 herein referred to as the driving gears. The toothed segment II of each driving gear is arranged to engage with the mutilated gear member I2 or the mutilated gear member I2 of a driven gear I3 which is displaceable in an axial direction on the sleeve I'I, I8 of a corresponding control disc I5, I6, the sleeved controldiscs being mounted on a shaft I4. Each driven gear I3 is splined on the corresponding sleeve I! or I8 so that the gears I3 which rotate with the control discs I5, I6 shall also be displaceable axially.

V The two mutilated driven gears I 2 and I2 of each driven gear I3 are arrahged side by side, each gear member I2 being mutilated at one point by the, cutting away of the teeth to form a gap, as at 20, which is of such extent that when it is. alined with the driving gear 9 or ID, as the case-may be, the driving gear may then operate idly. 'Similarly each gear member I2 is mutilated toiform a gap, as at I9, at a point diametrically opposite the gap 20 of the gear member I2, for the same purpose.

Each gear'segment II is provided at each end of its range of gear teeth I I with a wide toothZI, 22,; which projects on each side by about the width of the tooth portion II Secured to or formed integral with each driven gear I3 are two juxtaposed eccentrics 23, 2 1 which are displaced the one with respect to the other by degrees, the swell of each eccentric being formedtwith a notch 25, 26, diametrically opposed, adapted to be engaged by a spring loaded latchZl mounted in a guide 28 in order to hold the corresponding driven gear from rotary movement during the idling movement of the driving gear.

The hub of each driven gear I3 is provided with a peripheral groove 29 which is: engaged by a studjlof a corresponding bent lever 30, 3I mounted for oscillation on a stud 33. The arm 3| of each lever carries a roller 34 for coaction with the upper portion of a movable cam 36 at the right or 3'! at the left. The arm 30 of each such lever carries a roller 35 for coaction with the lower portion of the movable cam 36 or 31, as the case may be. The earns 36 and 31 are carried, respectively, by rods 38, 39 of an automatic pattern selector" device which is of usual construction and need not be shown or described herein. By such rod 38 or 39 the corresponding.

cam 36 or 37 is moved to cause the corresponding driven gear I3 to be displaced axially with respect to the driving gear II, so that the one driven gear member or the other. shall be engaged by the driving gear I I to effect rotation of the driven gear through 180 degrees, except when the gap I9 or 20 registers with the driving gear, at which time the driven gear is held from rotary movement by the latch 21. V

The control disc I6 has an eccentric 40 on which is mounteda disc M and on the disc M is mounted a ring 42 whichhas an extended arm 43. The latter has pivotally connected thereto one arm 44 of a bell crank lever which is pivotally mounted at 45, the other arm 46 of the bell crank lever being connected by a link 41 with the shuttle box, as diagrammatically shown in Figure 7, in which the different positions of the bell crank lever are represented by the broken lines I--IIIII--IV, with corresponding changes in the position of the shuttle box 48. The control disc I5 has secured thereto an eccentric pin 49 which engages a. radial groove 50 in the largest diameter of the disc 4I. Through the interrelation of the eccentric pins and discs as described the requisite movement is imparted to the bell crank lever 44, 46. It will be understood that the eccentric pin 49 moves in the radial groove 56 of the disc 5|.

In the operation of the mechanism illustrated in'Figures 1 -7 and above described, when the driving shaft 2 is made to rotate at the will of the operator, the rocker lever I by reason of the shape given to the cams 3 and 4 moves to and fro or reciprocates (in this instance with a swingingmotion) with a dwell after each half rotationof the shaft 2 and after each movement of the rocker lever I in one direction or the other. Continuing now the description of the interaction of the driving gear segment I 0 and the corresponding driven gear I3, since the two driving gear segments 9, I0 and the two driven gears I3 are the same in each case and it is unnecessary to describe both in detail, it will be understood that, as shown at the right hand in Fig-- ure 2, the driving-gear segment II), II is then in registration with the gap I9 of the gear member I2 and can reciprocate freely so long as *the driven gear I2"is held from rotation by engagement of the latch 21 with the notch'25 of the corresponding eccentric 23. If it be assumed that the shuttle change box 48 is then to be the left. The driving gear segment I 0 is then free to swing toward the right as indicated by the arrow in- Figure 1. In the displacement of the driven gear I3 to the left the gear member I2 of the driven gear I3 moves into engagement with the gear segment II], II alongside the gap I9, the retaining latch 27 being disengaged from the notch in the eccentric 23 in the initial movement of the gear I3 by reason of the engagement of the gear member I2 with the driving gear I0, I I. Through the continued engagement of the driving gear II), II with the gear member I2 the driven gear I3 is rotated through almost a half rotation in a clockwise direction, as seen in Figure 1, and as the swing of the driving gear segment I6, II approaches the limit of its swing to the right, as represented in Figure 5, the gap 20 of the gear member I2 is in registration with the driving gear segment Ii], II and the driven gear would remain at rest were it not that the end tooth 22 which projects at each side of the gear segment ID, II comes into engagement with the gear member I2 and effects a further turning of the driven gear I3 until a half rotation is completed. Thereupon the latch 21 engages with the notch 26 of the eccentric 24 and so holds the'driven gear I3 against further turning, the tooth 22having then passed out of engagement with the gear member.

During such half rotation of the driven gear I3 the eccentric 46 of the control disc I6 causes such movement of the eccentric ring 42 that the arm 43 of the eccentric ring 42 moves the bell crank lever 44, 46 from the position I, represented by full lines in Figure 7, to the position II, represented by dot and dash lines in Figure 7, whereby the shuttle change box 48 is moved downward through one unit of change.

As the driving gear II], II can now swing free in the gap 26, having an idling movement, the adjustment of the shuttle change box, effected as described above, continues until through the action of the pattern selector device the rod 38 is pulled upward and the driven gear I3 is again displaced to the right, into the position represented in Figures 2'and 3, the segmental driving gear II], II again assuming the position shown in Figure 1 in a swing to the left. At this time the driving gear I6, II leaves the gap 20 and engages the gear member I2 of the driven gear I3 and the operation already described is again repeated, the half rotation of the gear I3 being completed by-the action of the'wide tooth 22, whereupon the latch 2'! again engages the'notch 25 of the eccentric 23 and prevents' further rotation of the driven gear I3. In the second half rotation of the gear I3 the arm 43 is returned to the initial position and the bell crank 44, 43 is returned to the position I, represented by full lines in Figure 7, and the shuttle change box is returned to the corresponding initial position.

.To eiIect the shift of the shuttle change box 48 to the position III, also represented by dot and dash lines in Figure 7, which indicate the corresponding position of the bell'crank lever 44, 46, the right hand driven gear I3 remaining in the position last described, the left hand driven gear I3 is shifted to the right by the downward movement of the rod 39, through the action of the pattern selector device, into engagement with the segmental driving gear '9, I I. In this operati'onithe eccentric disc 4|, at that side of the mechanism, is turned through a half rotation, by the pen 49 which extends into the radial slot 53 of the eccentric disc M, the bell crank lever 44, 46 being shifted into the position III, also representedby dot and dash lines, and the change shuttle box 4 8'being moved into corresponding position. 9

To effect the change of the bell crank lever 44,46 to the position-IV, represented by the line selector device, with the result that the right.

hand driven 'gear I3 is shifted to the left and through the interaction of the gear segment IO, N and the right hand driven gear I3 the eccentric disc 40 is caused to have a half rotation.

It will be obvious that while in the operation already described the driving gear segments 9, l act on the driven gears only in one direction of swing, idling in the opposite direction of movement whereby the driven gear I3 is moved only in one direction of rotation, it may be arranged to have the driving gear segments 9, l0 operate in both directions or their movement, turning the driven gears iii in one direction during the forward swing and turning the gears in the opposite direction during the return swing. This adjustment requires no change in the mechanism described and is effected by movement of the rods 38, 39 effected by the pattern selector device so that each driven gear l3, having been shifted in one direction during the swing of the driving gear segment in one direction is shifted back to its initial position immediately on the completion of the movement of the corresponding driving gear segment in one direction, the two two end teeth 2|, 22 alternating in operation. For operation. in connection with a. loom which has a multi-shuttle box at only one side, the arrangement first described is sufiicient, the alternative arrangement last referred to being useful only in connection with looms which have a multi-ce1l shuttle change box for each side.

It will be understood that the occurrence of shocks in the operation of the improved mechanism is avoided because at each change the driven gear members which are alternatively in engagement with the driving gear segments lie adjacent to each other in all positions of operation with their ranges of gear teeth overlapping by at least one tooth.

In the embodiment of the invention illustrated in Figures 1-7 and described above the driving gear is formed as a gear segment and reciprocates with an oscillating or swinging movement. In the embodiment of the invention illustrated diagrammatically in Figure 8 the driving gear is moved to and fro or reciprocates in a right line, being formed as a straight bar guided, as at 52, and formed with toothed racks 53, 54.

In this instance the bar 5| has at one end a pin 55 in engagement with a groove 56 of an eccentric disc 51 on a driving shaft 58. Two driven gears l3 and 13 mounted on shafts M and [4 and composed each of two gear members l2 and i2, each having a gap, as at IS I9, 20, 20 diametrically opposed, are adapted for engagement, respectively, with the racks 53, 54. Each of such racks 53, 54 is provided at its ends with extended teeth 2 l 2N 22 22* which coact with the driven gears l3 and l3 in the same manner as already described with referenceto the construction illustrated in Figures The gear l3 is provided with an eccentric pin l3 to which is pivotally connected a link 60 which has pivotally connected thereto one end of a-lever 6| the other end of which is pivotallyconnected to the link 4'! which is connected to the shuttle change box 48 as before. The gear 13* similarly is provided with. an eccentricpin l3 which is connected by a link 59 with the fulcrum of the lever 6| It will be obvious that this embodiment of the invention is functionally the same as that shown in Figures 1-7, the essential change being in the substitution of a driving gear which reciprocates in a right line for the swinging driving gear of the construction shown in Figures 1-7.

In the embodiment of the invention shown somewhat diagrammatically in Figure 9, the reciprocating member is shown as a multiple gear segment 62, mounted on a shaft 8 and having rollers 5 and 6 which cooperate with cams 3 and-4 similar to the cams shown in Figure 1, and mounted on a driving shaft 2*. The gear segment moves to and fro or reciprocates or oscillates on its axis through the coaction of the cams 3 and 4 as described with reference to the embodiment of the construction shown in Figure 1. The driving gear segmenthas three toothed sectors 63, 64 and 65 with which are severally engaged driven gears l3 I3 and I3, each consisting of two driven gear members l2 and I2 which have gaps I9, 20 diametrically opposed as before. Each of the gears l3 and l3 and I3 is provided with an eccentric pin l3. Connected to the pin l3 of the gear I3 is a link 88 to which is connected pivotally one end'of a lever 10, the other end of which is connected to the link 41 which in turn is connected to the multi-cell shuttle change box 48. The eccentric pin Hi of the gear i3 is connected, as at B9, to the fulcrum of the lever 10, which it carries. The other end of the lever 69 is connected by a link 66 to the eccentric pin l3 of the driven gear I3 Each of the tooth sectors 63, 64 and 65 is provided at its ends with wide teeth 2 l 22, which coact with the gear members l2 and l2 of the driven gears 13 I3 and 13 in the same manner as already described with reference to the wide teeth 2|, 22 of the driving gears 9, II and I0, ll shown in Figure 1. Through the properly timed coaction of .the several gear sectors 63, 64 and 65, which are shifted in an axial direction, as hereinbefore described, under the control of the pattern device, and through the interaction of the levers 69 and the shuttle change box 68 can be shifted to place any one of the several cells in line with the loom shed.

Other embodiments of the invention, all functioning in the same manner will readily suggest themselves to meet different conditions of operation and it will be understood that, except as pointed out in the accompanying claims, the invention is not restricted to the particular construction shown and described herein.

I claim as my invention:

1. In a shuttle box mechanism for looms, the combination of a shuttle box, a reciprocating driving gear, a driven gear for engagement with the driving gear and having diametrically opposed tooth gaps, each of which permits idling movement of the driving gear, a special tooth at the end of the range of gear teeth of the driving gear, which special tooth is wider in an axial direction than the gear teeth and by which the rotation of the driven gear is completed to a half rotation, and operative connections from the driven gear to the shuttle box.

2. In a shuttle box mechanism for looms, the

combination of a shuttle box, a plurality of reciprocating driving gears, a plurality of driven gears for engagement with thedriving gears respectively and having diametrically opposed tooth gaps each of which permits idling movement of the corresponding driving gear, a special tooth at the end of the range of gear teeth on each driving gear, which special tooth is wider in an axial direction than the gear teeth and by which the rotation of each driven gear is completed to a half rotation, and operative connections from the driven gears to the shuttle box.

3. In a shuttle box mechanism for looms, the combination of a shuttle box, a reciprocating segmental driving gear, a driven gear for engagement with the driving gear and having diametrically opposed tooth gaps, each of which permits idling movement of the driving gear, a special tooth at the end of the range of gear teeth of the driving gear which is wider in an axial direction than the gear teeth and by which the rotation of the driven gearis completed to a half rotation, and operative connections from the driven gear to the shuttle box.

4. In a shuttle box mechanism for looms, the combination of a shuttle box, a rack bar reciprocating in a right line, a driven gear for engagement with the rack bar and having diametrically opposed tooth gaps, each of which permits idling movement of the rack bar, a special tooth at the end of the range of gear teeth of the rack bar, which is wider in an axial direction than the gear teeth of the rack bar and by which the rotation of the driven gear is completed to a half rotation, and operative connections from the driven gear to the shuttle box.

GEORG WIGET. 

